JP3331765B2 - Air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner having an improved operation control system in a dehumidifying mode.

[0002]

2. Description of the Related Art In recent years, an air conditioner mounted on an electric vehicle, for example, uses a refrigeration cycle that also serves as a heat pump, and switches between cooling and heating by switching a circulation path of a refrigerant by a valve.

[0003]

The applicant of the present invention discloses a condenser and an evaporator in a ventilation duct as disclosed in Japanese Patent Application No. Hei 4-107070 in order to perform the operation from cooling and heating to dehumidification in such a refrigeration cycle also used as a heat pump. And an outdoor heat exchanger is arranged outside the blower duct, the condenser, the outdoor heat exchanger, and the evaporator are provided in a refrigerant circuit, and a valve provided in the refrigerant circuit is switched to switch the refrigerant. An air conditioner configured to switch the operation mode to one of cooling, heating, and dehumidification by switching the circulation path as follows is proposed. That is, in the cooling mode, the refrigerant discharged from the compressor flows from the outdoor heat exchanger to the evaporator and returns to the compressor, so that the outdoor heat exchanger functions as an “outdoor condenser”. In the heating mode, the refrigerant discharged from the compressor flows from the condenser to the outdoor heat exchanger and returns to the compressor, so that the outdoor heat exchanger functions as an “outdoor evaporator”. Furthermore, in the dehumidification mode, the refrigerant discharged from the compressor flows from the condenser to the evaporator via the outdoor heat exchanger, and the air dehumidified and cooled by the evaporator is reheated to the target blowing temperature by the condenser and blown into the vehicle interior. ing.

In such an air conditioner, an outdoor fan for forcibly blowing air to an outdoor heat exchanger is provided in order to control the blowing temperature during cooling, heating, and dehumidification, and the number of rotations of the outdoor fan is switched. , By changing the heat exchange capacity (heat absorption capacity or heat dissipation capacity) of the outdoor heat exchanger,
The heat radiation capability of the capacitor and the heat absorption capability of the evaporator are changed.

When the above-described air conditioner is installed in a vehicle such as a one-box car, the heat exchange capacity of the outdoor heat exchanger is set because the outdoor heat exchanger is mounted horizontally on the lower surface of the vehicle body. Has the characteristic that it is hardly affected by the wind speed of the vehicle (wind that is received as the vehicle travels). Therefore, by changing the rotation speed of the outdoor fan, the heat exchange capacity of the outdoor heat exchanger is actively increased. It is possible to control.

On the other hand, in a case where the air conditioner is installed in a normal vehicle, that is, a vehicle in which the vehicle wind is sucked from the front grill, a position where the outdoor heat exchanger receives the vehicle wind from the front grill. If attached to
Since the heat exchange capacity of the outdoor heat exchanger fluctuates according to the magnitude of the vehicle speed, the following problems occur.

That is, in the cooling mode and the heating mode, even when the heat exchange capacity of the outdoor heat exchanger fluctuates, in each mode, the temperature of the evaporator that works as the cooling heat exchanger and the temperature of the condenser that works as the heating heat exchanger. Since the temperature does not fluctuate so much, the temperature of the conditioned air does not fluctuate greatly, and no practical problem occurs.

However, in the dehumidification mode in which the condenser acts as a reheating source for the wind dehumidified and cooled by the evaporator, the condenser and the outdoor heat exchanger function as a refrigerant condenser in a state of being connected in series. A phenomenon occurs in which the temperature of the capacitor fluctuates according to the magnitude. That is, when the vehicle speed is high, the heat radiation performance in the condenser and the outdoor heat exchanger, and consequently, the condensation performance is increased and the condensing pressure is reduced, so that the temperature of the condenser is relatively lowered, and the vehicle speed is low. In this case (including when the vehicle is stopped), the condensation performance in the condenser and the outdoor heat exchanger is reduced and the condensation pressure is increased, so that the temperature of the condenser is relatively increased. For this reason, in the dehumidification mode, the blowing temperature depending on the temperature of the condenser is
There is a problem that the air conditioner changes depending on the speed of the vehicle, so that comfortable air conditioning cannot be expected.

On the other hand, the adjustment range of the heat exchange capacity of the outdoor heat exchanger obtained by switching the rotation speed of the outdoor fan is not sufficient in view of the actually required temperature adjustment range of the blown air. However, there was also a disadvantage that it was narrow.

The present invention has been made in view of such circumstances, and an object of the present invention is to perform a process from cooling and heating to dehumidification by a refrigeration cycle which also serves as a heat pump. Even when mounted in a state that affects the heat dissipation system of the refrigeration cycle, it is possible to effectively prevent a situation in which the blowout temperature in the dehumidification mode fluctuates due to the magnitude of the vehicle speed, and it is possible to always perform comfortable air conditioning operation, Another object of the present invention is to provide an air conditioner capable of expanding the temperature control range of the blown air in the dehumidification mode and improving the temperature controllability in the dehumidification mode.

[0011]

In order to achieve the above object, an air conditioner according to the present invention comprises, in a refrigerant circuit, an evaporator disposed in a blower duct and a heating source for wind passing through the evaporator. A functioning condenser and an outdoor heat exchanger disposed outside the air duct are provided, and a first throttle is provided in a refrigerant flow path between the condenser and the outdoor heat exchanger, and the outdoor heat exchanger is provided. A second throttle is provided in a refrigerant flow path between a heater and the evaporator, and a valve provided in the refrigerant circulation circuit is switched to switch a circulation path of the refrigerant, so that the operation mode is any of cooling, heating, and dehumidification. In a dehumidification mode, refrigerant is transferred from the condenser through the first throttle, the outdoor heat exchanger, and the second throttle in this order to the air. It is obtained by configured to flow into porator (claim 1).

In this case, both the first and second diaphragms can be constituted by fixed diaphragms.

Further, at least the first diaphragm of the first diaphragm and the second diaphragm is constituted by a variable diaphragm, and the diaphragm opening of the first diaphragm is adjusted in the dehumidification mode to thereby control the evaporator. The temperature of the capacitor and the temperature of the capacitor may be adjusted (claim 3).

In the case where at least the first throttle is constituted by a variable throttle as described above, the structure is such that the rotation speed of a compressor provided in the refrigerant circulation circuit can be adjusted, and at least the first throttle is in the dehumidification mode. It is also possible to provide a control means for controlling the throttle opening and controlling the number of revolutions of the compressor (claim 4).

In this case, in the dehumidification mode, the control means controls at least the number of revolutions of the compressor so that the temperature of the evaporator becomes a set value, and the temperature of the air blown from the air duct becomes a predetermined value. Thus, at least the aperture of the first aperture can be adjusted (claim 5).

[0016] In the dehumidification mode, the control means includes:
At least the number of rotations of the compressor is controlled so that the temperature difference between the upstream air temperature of the evaporator and the air temperature after passing through the evaporator becomes a predetermined value, and the temperature of air blown from the air duct becomes a predetermined value. Alternatively, at least the aperture of the first aperture may be adjusted (claim 6).

In the dehumidification mode, the control means includes:
At least the rotation speed of the compressor is controlled so that the temperature difference between the outdoor temperature and the air temperature after passing through the evaporator is a predetermined value, and at least the first temperature is controlled so that the temperature of air blown from the air duct becomes a predetermined value. It is also possible to adopt a configuration in which the degree of opening of the diaphragm is adjusted.

In the dehumidification mode, the control means includes:
During the period from the start of the dehumidification operation to the elapse of the predetermined time, at least the rotation speed of the compressor is controlled so that the temperature of the evaporator becomes a set value, and the temperature of the air blown from the air duct becomes the predetermined value. At least the throttle opening of the first throttle is adjusted, and after the predetermined time has elapsed, at least the temperature difference between the upstream air temperature of the evaporator and the air temperature after passing through the evaporator becomes a predetermined value. In addition to controlling the number of revolutions of the compressor, it is also possible to adopt a configuration in which at least the aperture of the first throttle is adjusted so that the temperature of air blown from the air duct becomes a predetermined value (claim 8).

Further, both the first diaphragm and the second diaphragm are constituted by variable diaphragms, and the combination of the diaphragm openings of these diaphragms is set in a plurality of stages. In the method, the temperature of the evaporator and the temperature of the condenser are corrected by correcting the combination of the opening degrees of the first and second throttles every time a predetermined time elapses based on information indicating the temperature of air blown from the air duct. Can be adjusted (claim 9).

[0020]

According to the first aspect of the invention, in the dehumidification mode, the refrigerant discharged from the compressor flows from the condenser to the evaporator via the first throttle, the outdoor heat exchanger, and the second throttle in this order, and is dehumidified by the evaporator. The cooled air is reheated to the target blowing temperature by utilizing the heat generated by the condenser and blown into the room. In such a dehumidification mode, the condenser and the outdoor heat exchanger function as a refrigerant condenser in a state of being connected in series, but actually, the first heat exchanger is provided between the condenser and the outdoor heat exchanger. Is provided, so that most of the refrigerant discharged from the compressor is condensed by the condenser, and the heat of the condensation is exchanged with the air dehumidified and cooled by the evaporator. . Therefore, the outdoor heat exchanger is in a state where a relatively low-temperature refrigerant flows in, that is, a state in which the difference between the temperature of the refrigerant flowing into the outdoor heat exchanger and the outside air temperature is small is exhibited. Can be regarded as mere refrigerant passage piping. As a result, when the air conditioner is mounted on a vehicle, the temperature of the condenser in the dehumidification mode depends on the magnitude of the vehicle speed even when the outdoor heat exchanger is arranged in a state of receiving the wind accompanying the traveling of the vehicle. The temperature of the blown air after being reheated by the condenser becomes stable.

According to the second aspect of the present invention, since both of the first and second diaphragms are constituted by fixed diaphragms, their structures can be simplified, which contributes to a reduction in manufacturing cost. The number of movable parts can be reduced, and the reliability over the life can be improved.

On the other hand, the blowout temperature in the dehumidification mode is determined by three factors: the intake air temperature, the heat absorption capacity of the evaporator, and the heat dissipation capacity of the condenser.
What is necessary is just to adjust the heat absorption capacity of the evaporator and the heat dissipation capacity of the condenser. In order to realize this, in the invention according to claim 3, the first restriction between the condenser and the outdoor heat exchanger is a variable restriction. Adjust the throttle opening (flow path resistance). As a result, the pressure of both the condenser and the outdoor heat exchanger changes, and both the temperature of the condenser (radiation capacity) and the temperature of the outdoor heat exchanger change. As a result, when the temperature of the outdoor heat exchanger is sufficiently higher than the outside air temperature, the heat radiation capability of the outdoor heat exchanger as an “outdoor capacitor” increases, and the heat radiation capability of the capacitor relatively decreases. Further, when the temperature of the outdoor heat exchanger approaches the outside air temperature, the heat radiation capability of the outdoor heat exchanger as an “outdoor capacitor” decreases, and the heat radiation capability of the capacitor relatively increases. Furthermore, when the temperature of the outdoor heat exchanger becomes substantially the same as the outside air temperature, the outdoor heat exchanger is in a state where it hardly exchanges heat with the outside air (mere refrigerant passage).

Further, if the control means for adjusting at least the opening degree of the first throttle and the number of rotations of the compressor in the dehumidification mode is provided, the refrigerant discharge pressure of the compressor can be reduced. The temperature of the evaporator can be adjusted, and the temperature of the evaporator is controlled to an appropriate temperature while controlling the temperature of the evaporator so as to ensure a sufficient dehumidifying capacity within a range not excessively cooled, so that the temperature of the blown air becomes the target blowout temperature. Can be controlled.

According to a fifth aspect of the present invention, in the dehumidification mode, the control means controls the number of revolutions of the compressor such that the temperature of the evaporator becomes a set value when adjusting the number of revolutions of the compressor as described above. And
Further, in adjusting the aperture of at least the first throttle as described above, the aperture of the first throttle is adjusted so that the temperature of air blown from the air duct becomes a predetermined value. It is possible to keep the temperature of the condenser at an optimum state while keeping the temperature of the evaporator stable, and as a result, the temperature of the blown air can be accurately controlled.

According to the sixth aspect of the present invention, in the dehumidification mode, the control means adjusts the compressor speed as described above, and determines the temperature difference between the air temperature upstream of the evaporator and the air temperature after passing through the evaporator. Is controlled to a predetermined value, the rotation speed of the compressor is controlled,
In adjusting at least the opening of the first throttle, the opening of the first throttle is adjusted so that the temperature of air blown from the air duct becomes a predetermined value. The temperature of the condenser can be maintained at an optimum state while maintaining a state where the exchange capacity is stabilized. As a result, the temperature of the blown air can be accurately controlled.

According to the present invention, in the dehumidification mode, when adjusting the compressor speed as described above, the control means may adjust the temperature difference between the outdoor temperature and the air temperature after passing through the evaporator to a predetermined value. Control the number of rotations of the compressor so that at least
In adjusting the throttle opening of the first throttle, since the throttle opening of the first throttle is adjusted so that the temperature of air blown from the air duct becomes a predetermined value, the outdoor air is subjected to heat exchange with the evaporator. Even if the air is blown out indoors, the temperature of the condenser can be maintained at the optimum state while keeping the heat exchange capacity of the evaporator stable, so that the temperature of the blown air can be controlled accurately. Become.

According to the present invention, in the dehumidification mode, the control means adjusts the compressor speed as described above and adjusts at least the aperture of the first throttle from the start of the dehumidification operation. During the period until the predetermined time elapses, the number of rotations of the compressor is controlled so that the temperature of the evaporator becomes the set value, and the opening degree of the first throttle is adjusted so that the temperature of the air blown from the air duct becomes the predetermined value. In addition, after the predetermined time has passed, while controlling the rotation speed of the compressor so that the temperature difference between the air temperature on the upstream side of the evaporator and the air temperature after passing through the evaporator becomes a predetermined value, The throttle opening of the first throttle is adjusted so that the temperature of air blown from the duct becomes a predetermined value. Therefore, at the beginning of defrosting,
While keeping the temperature of the evaporator stable, the temperature of the capacitor can be maintained at the optimum state,
After a lapse of a predetermined time from the start of defrosting, the temperature of the condenser can be maintained at an optimum state while maintaining the heat exchange capacity of the evaporator, resulting in more accurate control of the temperature of the blown air. Will be able to do it.

Further, both the first diaphragm and the second diaphragm are constituted by variable diaphragms, and in the dehumidification mode, the combination of the diaphragm opening degrees of the respective diaphragms is determined. If the configuration is such that the temperature is corrected based on the information indicating the blowout temperature from the air duct every certain time, the actual blowout temperature can approach the target blowout temperature every certain time. Thus, it is possible to greatly improve the control characteristics of the blowout temperature.

[0029]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment in which the present invention is applied to an air conditioner for an electric vehicle will be described with reference to FIGS. First, a schematic configuration of the entire air conditioner will be described with reference to FIG.

On the upstream side of the air duct 21, there are provided an outside air inlet 22 for sucking air (outside air) outside the vehicle compartment and two inside air inlets 23, 24 for sucking air (inside air) inside the vehicle compartment. I have. An inside / outside air damper 25 is provided at an intermediate portion between the inside air intake port 23 and the outside air intake port 22. The opening degree of the inside / outside air damper 25 is adjusted by a servo motor 26, so that the outside air intake port 22 Inlet 23, 2
The intake air temperature is adjusted by varying the mixing ratio of the air to be taken in from step 4. Blowers 2 are provided downstream of the inside / outside air damper 25 and downstream of the inside air suction port 24, respectively.
7 and 28 are provided, and these two blowers 27 and 28 are attached to the rotating shaft of a blower motor 29. The blower motor 29 is driven by a drive circuit 30.

On the other hand, an evaporator 31 is disposed downstream of the blowers 27 and 28, and the downstream of the evaporator 31 is partitioned by a partition plate 32 into two upper and lower ventilation paths 33 and 34. A condenser 35 is disposed in the lower ventilation path 34, and an upper portion of the condenser 35 projects into the upper ventilation path 33. This capacitor 35
A strong cooling damper 36 is arranged above the above. By driving the strong cooling damper 36 by a servomotor 37,
The amount of air that bypasses the condenser 35 is variable. Further, the partition plate 32 on the downstream side of the condenser 35
A communication damper 38 is disposed in a communication port 32a provided in the partition plate 32. The communication damper 38 is driven by a servomotor 39 to vary the amount of air passing through the communication port 32a of the partition plate 32, thereby achieving a single mode. (Eg "FACE"
Mode, “DEF” mode, etc.).

Downstream of the upper ventilation passage 33, a DEF outlet 40 and a FACE outlet 41 are provided. The FACE outlet 41 and the DEF outlet 40 are provided with dampers 48 and 49, respectively.
49 is driven by servo motors 50 and 51. On the other hand, on the downstream side of the lower ventilation path 34,
A FOOT outlet 52 for blowing the wind toward the feet of the occupant is provided, and a damper 54 driven by a servomotor 53 is also provided on the FOOT outlet 52.

On the other hand, the above-described evaporator 31 and condenser 35 are components of a refrigeration cycle 55 that also serves as a heat pump. As shown in FIG. 1, the refrigerant circulation circuit of the refrigeration cycle 55 includes a compressor 56, a four-way switching valve 57, an outdoor heat exchanger 58, a check valve 59, a capillary 61, a solenoid valve 62, an electronic expansion valve 65, an accumulator 9
0, an evaporator 31 and a condenser 35 are connected by piping, and an electronic expansion valve 65 (as a first restriction in the present invention) is provided as a variable restriction in a refrigerant flow path between the condenser 35 and the outdoor heat exchanger 58. A capillary 61 (corresponding to a second throttle in the present invention) is provided as a fixed throttle in the refrigerant flow path between the outdoor heat exchanger 58 and the evaporator 31. The solenoid valve 62 and the electronic expansion valve 6
The five-way and four-way switching valves 57 are switched as shown in Table 1 below according to the operation mode of the refrigeration cycle 55.

[0034]

[Table 1]

As is apparent from Table 1, in the cooling mode, the solenoid valve 62 is turned off, the electronic expansion valve 65 is fully closed, and the four-way switching valve 57 is moved to the position indicated by the dotted line in FIG. ), And the refrigerant discharged from the discharge port 56a of the compressor 56 circulates in the route of the check valve 59 → the outdoor heat exchanger 58 → the capillary 61 → the evaporator 31 → the accumulator 90 → the suction port 56b of the compressor 56. Thus, the high-temperature gas refrigerant discharged from the discharge port 56a of the compressor 56 is supplied to the outdoor heat exchanger 58.
Then, the liquid refrigerant is liquefied by heat, and the liquid refrigerant is evaporated by the evaporator 31, so that the wind passing through the evaporator 31 is cooled.

On the other hand, in the heating mode, the solenoid valve 62 is turned on, the four-way switching valve 57 is switched to the position (off position) shown by the solid line in FIG. 1, and the electronic expansion valve 65 is controlled to an arbitrary throttle opening. And the outlet 5 of the compressor 56
The refrigerant discharged from 6a circulates through the path of the condenser 35 → the electronic expansion valve 65 → the outdoor heat exchanger 58 → the electromagnetic valve 62 → the accumulator 90 → the suction port 56b of the compressor 56. As a result, the high-temperature gas refrigerant discharged from the discharge port 56a of the compressor 56 dissipates heat and liquefies in the condenser 35, and the heat that passes through the condenser 35 is warmed.

In the defrosting mode, the solenoid valve 62 is turned off, the electronic expansion valve 65 is fully opened, and the four-way switching valve 57 is switched to the position shown by the solid line in FIG. Is discharged to the outdoor heat exchanger 58 via the condenser 35 and the electronic expansion valve 65 to remove frost on the surface of the outdoor heat exchanger 58.

Further, in the dehumidification mode, the electromagnetic valve 62 is turned off, the four-way switching valve 57 is switched to the position shown by the solid line in FIG. 1, and the electronic expansion valve 65 is controlled to an arbitrary throttle opening. As a result, the flow path of the refrigerant flows from the condenser 35 → the electronic expansion valve 65 → the outdoor heat exchanger 58 → the capillary 61 → the evaporator 31;
The resistance of the flow path in the refrigerant flow path from the flow path to the outdoor heat exchanger 58 is arbitrarily switched by the electronic expansion valve 65.

The outdoor heat exchanger 58 is provided with an outdoor fan 89 for forced cooling. The fan motor 89a of the outdoor fan 89 has a refrigeration cycle 5 as shown in FIG.
5, high-speed rotation "Hi", low-speed rotation "Lo", and stop "OF" based on the output data of various sensors described later.
For example, in the cooling mode, the outside air temperature Tam detected by the outside air temperature sensor 78 becomes “Hi” at 25 ° C. or higher and “Lo” at 22 ° C. or lower. In the heating mode, the outside air temperature Tam
Becomes “Hi” below 13 ° C. and “Lo” above 16 ° C.
Becomes In the dehumidification mode, the refrigerant discharge pressure sensor 8
8, the refrigerant discharge pressure P of the compressor 56 detected by
d, depending on the refrigerant discharge temperature Td of the compressor 56, Hi
>Lo> OFF. For example, if the refrigerant discharge pressure Pd is 19 kgf / cm ² G or more, T
No matter what value d is, it will always be "Hi".

On the other hand, the compressor 5 of the refrigeration cycle 55
The rotation speed of the motor 66 that drives the motor 6 is controlled by the inverter 67. The inverter 67, the servo motors 26, 37, 39, 50, 51, 53, the fan motor 89 a of the outdoor fan 89, and the drive circuit 30 of the blower motor 29 are controlled by an electronic control unit (hereinafter referred to as “ECU”) 68. This ECU 68 is mainly composed of a microcomputer,
9, a RAM 70 for temporarily storing various data, a ROM 71 for storing the control program of FIG.
A / D converter 7 for converting input data into digital values
2, an I / O unit 73, a crystal unit 74 for generating a reference signal of several MHz, and the like, and power is supplied from a battery 75 via an ignition switch 76.

The ECU 68 includes an inside air temperature sensor 77 for detecting the inside air temperature Tr, an outside air temperature sensor 78 for detecting the outside air temperature Tam, a solar irradiation sensor 79 for detecting the amount of sunlight Ts entering the vehicle interior, and an air temperature immediately after passing through the evaporator 31. An evaporator outlet temperature sensor 80 for detecting Te (hereinafter referred to as "evaporator outlet temperature"), a condenser outlet temperature sensor 81 for detecting air temperature immediately after passing through the condenser 35 (hereinafter referred to as "condenser outlet temperature") Tc, and refrigerant discharge of the compressor 56. The refrigerant discharge pressure sensor 88 for detecting the pressure Pd, the temperature setting device 82 for the occupant to manually set the set temperature sense Sset as a control target, and the evaporator 3
1, the intake air temperature sensor 46 for detecting the temperature of the air sucked into the evaporator 31 (hereinafter referred to as "intake air temperature") Tin, the discharge temperature sensor 91 for detecting the refrigerant discharge temperature Td, and the condenser outlet refrigerant temperature Tcr. Is detected via an A / D converter 72 from a condenser outlet refrigerant temperature sensor 92 or the like for detecting the temperature.

The above-mentioned warm feeling setting device 82 is provided with the cooling key 8
2A and a warming key 82b are provided on an air conditioner control panel 83 arranged at the center of an instrument panel (not shown) of the vehicle. As shown in FIG. 2, the air conditioner control panel 83
Above the warm feeling setting device 82, a warm feeling display section 84 in which a plurality of light emitting elements 84n are arranged in a horizontal line is provided. The warm feeling display section 84 displays the set warm feeling Sset input by the cool key 82a and the warm key 82b. This set temperature sensation Sset is an index indicating how much to cool or warm up based on the average temperature of 25 ° C. [see FIG. 5 (a)], and before the keys 82a and 82b are operated. In the state, the light emitting element 8 at the center of the warm feeling display section 84
4n is turned on, and each time the cool key 82a is pressed once,
Reduce the set thermal sensation Sset by one rank and set the lighting position to 1
Each time the warming key 82b is pressed once, the set temperature sensation Sset is raised by one rank and the lighting position is shifted one position to the right. In addition, the air conditioner control panel 83 is provided with an air conditioner on / off switch 85, a rear defogger switch 86, and a front defroster switch 87.

On the other hand, the ECU 68 executes the control program shown in FIG. 4 to control the entire air conditioning operation, and at the time of the dehumidification mode, the electronic expansion valve 65 as described later.
It also functions as control means for controlling the throttle opening and the rotation speed of the compressor 56.

Hereinafter, the control contents of the ECU 68 will be described with reference to the flowchart of FIG. First, step 10
At 0, after executing an initialization process for initializing a counter and a flag to be used for the subsequent calculation process, the process proceeds to step 110 to read the set temperature sensation Sset inputted by operating the temperature sensation setting device 82 and , The outside air temperature Tam, the amount of solar radiation T detected by the various sensors described above.
s, evaporator outlet temperature Te, condenser outlet temperature T
c, refrigerant discharge pressure Pd, intake air temperature Tin, refrigerant discharge temperature T
d, read each data of the condenser outlet refrigerant temperature Tcr.

Next, the routine proceeds to step 120, where the set temperature Tset is obtained from the set temperature sensation Sset, the outside air temperature Tam and the amount of solar radiation Ts by the following equation (1). Tset = f (Sset, Tam, Ts) = Tset ′ + ΔTam + ΔTs (1) Here, Tset ′ = 25 + 0.4 Sset (see FIG. 5A) ΔTam = (10−Tam) / 20 (FIG. 5) See b) ΔTs = −Ts / 1000 See FIG. 5 (c)

After calculating the set temperature Tset as described above, the routine proceeds to step 130, where the set temperature Tset is set in the vehicle interior.
The amount of heat QAO required to maintain set is calculated by the following equation (2). QAO = K1 × Tset−K2 × Tr−K3 × Tam−K4 × Ts + C (2) (K1, K2, K3, K4: coefficient, C: constant)

After calculating the required heat quantity QAO according to the equation (2), the routine proceeds to step 140, where the front defroster switch 87 is turned on (hereinafter referred to as "DEF input").
Is determined. If there is no DEF input, the routine proceeds to step 150, where the required heat quantity Q shown in FIG.
The air volume VB is obtained from the air volume characteristics for AO, and this air volume V
Let B be the blowing air volume VAO. Then, in step 160,
The target outlet temperature TAO (condenser target outlet temperature) is calculated by the following equation (3).

TAO = QAO / (Cp · γ · VAO) + Tin (3) where Cp is the specific heat of air, γ is the specific gravity of air, and Tin is the intake air temperature sucked into the evaporator 31.

Thereafter, at step 170, the inside air inlet 2
The opening degree of the inside / outside air damper 25 is calculated so as to reduce the temperature difference between the temperature (intake temperature) Tin of the air sucked from the outside air intake port 3 and the outside air intake port 22 and the outlet temperature TAO. Then
In step 180, it is determined from the following equation (4) whether to set the operation mode of the refrigeration cycle 55 to the cooling (blowing) or heating mode.

TM = TAO−Tin (4) When the value of TM obtained by the equation (4) is TM ≧ + θ (for example, θ = 2 ° C.), the heating mode is set, and TM ≦
When −θ, the cooling mode is set, and when −θ <TM <+ θ, the compressor 56 of the refrigeration cycle 55 is stopped.

After the operation mode of the refrigeration cycle 55 is determined in this way, the routine proceeds to step 190, where the dampers 36, 38,.
The opening degrees of 46, 48, 49 and 54 are determined, and the blowing mode is set to “FACE”, “B / L”, “FOOT”, “FOOT”.
/ DEF "or" DEF ". The above is the processing when there is no DEF input.

On the other hand, if there is a DEF input, the flow shifts from step 140 to step 155 to set the blowing air volume VAO at the time of DEF to, for example, 300 m ³ / h. Next, in step 165, the opening degree of the inside / outside air damper 25 is determined to be in the outside air mode, and in step 175, the target outlet temperature TAO (condenser target outlet temperature) is calculated by the above-described equation (3).

Next, at step 185, it is determined in the same manner as described above whether the operation mode of the refrigeration cycle 55 is the cooling mode or the heating mode (however, if there is a DEF input, the air blowing mode is performed). Absent). Thereafter, the process proceeds to step 195, and determines that the blowing mode is “DEF”, and then proceeds to step 200.

In step 200, the branch destination is determined to be one of steps 210, 220, and 230 according to the operation mode determined in step 180 or 185 described above. That is, in the cooling mode, the process proceeds to step 210, and outputs various control data to each device.
In step 1, the rotational speed of the compressor 56 is feedback-controlled by PI control or fuzzy control with respect to the evaporator outlet temperature Te detected by the evaporator outlet temperature sensor 80. At this time, the blower voltage to be applied to the blower motor 29 in order to realize the blown air amount VAO determined in step 150 is determined according to the blow mode according to the voltage characteristics of FIG. In addition, when there is no DEF input, the compressor 56 is stopped and only the air is blown when the blowing air of the target blowing temperature TAO can be generated by mixing the inside air and the outside air. 56 is operated to perform dehumidification and cooling.

On the other hand, in the heating mode, the process proceeds to step 220 to output various control data to each device, and in step 221 the compressor outlet temperature Tc detected by the capacitor outlet temperature sensor 81 is targeted for the compressor 56 to operate. The rotational speed is feedback-controlled by PI control or fuzzy control, and in step 222, the condenser outlet refrigerant temperature Tcr detected by the condenser outlet refrigerant temperature sensor 92 and the refrigerant discharge pressure of the compressor 56 detected by the refrigerant discharge pressure sensor 88. The throttle opening of the electronic expansion valve 65 is controlled so that the subcool of the capacitor 35 calculated from Pd becomes appropriate. The opening degree characteristic of the electronic expansion valve 65 is set such that when the valve stroke exceeds a predetermined value ST1, as shown in FIG.

In the dehumidification mode, the routine proceeds to step 230, where the evaporator target outlet temperature Teo is calculated so as to satisfy, for example, the intake air temperature Tin-15 ° C. and 3 ° C. or higher. Is output. Next, at step 232, the evaporator outlet temperature Te detected by the evaporator outlet temperature sensor 80.
Is controlled so that the temperature of the evaporator reaches the evaporator target outlet temperature Teo.
In step 3, the throttle opening of the electronic expansion valve 65 is controlled so that the condenser outlet temperature Tc detected by the condenser outlet temperature sensor 81 becomes the target outlet temperature TAO (condenser target outlet temperature). At this time, the rotation speed of the compressor 56, the evaporator outlet temperature Te, and the condenser outlet temperature T
c, the relationship between the throttle opening of the electronic expansion valve 65 is shown in FIG.

In this case, when the throttle opening of the electronic expansion valve 65 is adjusted, the pressure of both the condenser 35 and the outdoor heat exchanger 58 changes, and the temperature (radiation capacity) of the condenser 35 and the outdoor heat exchanger 58 The temperature changes together. This allows
If the temperature of the outdoor heat exchanger 58 becomes sufficiently higher than the outside air temperature, the heat radiating ability of the outdoor heat exchanger 58 as an “outdoor capacitor” increases, and the heat radiating capacity of the capacitor 35 relatively decreases. When the temperature of the outdoor heat exchanger 58 approaches the outside air temperature, the heat radiation capability of the outdoor heat exchanger 58 as an “outdoor capacitor” decreases, and the heat radiation capability of the capacitor 35 relatively increases. Further, when the temperature of the outdoor heat exchanger 58 becomes substantially the same as the outside air temperature, the outdoor heat exchanger 58 is in a state where it hardly exchanges heat with the outside air (mere refrigerant passage).

As described above, by adjusting the degree of opening of the electronic expansion valve 65 to change the heat exchange function of the outdoor heat exchanger 58, the heat radiation capability of the condenser 35 and the evaporator 3
1, the heat absorption capacity can be adjusted in a relatively wide range, and the temperature control range of the blown air in the dehumidification mode can be expanded,
The temperature controllability in the dehumidification mode can be improved.

Further, in the present embodiment, in the dehumidification mode, the rotation speed of the compressor 56 is adjusted together with the throttle opening of the electronic expansion valve 65, so that the refrigerant discharge pressure of the compressor 56 can be adjusted. The synergistic effect of adjusting the opening degree of the expansion valve 65 can control both the evaporator outlet temperature Te and the condenser outlet temperature Tc to appropriate temperatures. As a result, the condenser outlet temperature T e is controlled while controlling the evaporator outlet temperature Te so as to ensure a sufficient dehumidifying capacity within a range not excessively cooled.
By controlling c to an appropriate temperature, the temperature of the blown air can be controlled to be the target blowout temperature TAO, and the comfort in the dehumidification mode can be further improved.

In the above embodiment, when the outdoor heat exchanger 58 is arranged in a state of receiving the wind accompanying the running of the electric vehicle, for example, the difference between the temperature of the outdoor heat exchanger 58 and the outside air temperature is determined. If a configuration is adopted in which the degree of opening of the electronic expansion valve 65 is changed to be small when the temperature becomes larger than the preset temperature range, the following operation and effect can be obtained. .

That is, in the dehumidification mode, the condenser 35 and the outdoor heat exchanger 58 function as a refrigerant condenser in a state of being connected in series, but between the condenser 35 and the outdoor heat exchanger 58, Since there is an electronic expansion valve 65 adjusted to a state where the throttle opening is small, the compressor 5
Most of the refrigerant discharged from the condenser 6 is condensed by the condenser 35, and the heat of condensation is transferred to the evaporator 31.
The heat is exchanged with the dehumidified and cooled air. Therefore, since a relatively low-temperature refrigerant flows into the outdoor heat exchanger 58, that is, a state in which the difference between the temperature of the refrigerant flowing into the outdoor heat exchanger 58 and the outside air temperature is reduced,
The outdoor heat exchanger 58 can be regarded as a mere refrigerant passage pipe. As a result, even when the outdoor heat exchanger 58 is arranged in a state of receiving the wind accompanying the traveling of the electric vehicle, the temperature of the condenser 35 in the dehumidifying mode hardly fluctuates according to the magnitude of the vehicle speed.
Since the temperature of the blown air after the heat exchange becomes stable, comfortable air conditioning can be expected.

In the above embodiment, the opening characteristic of the electronic expansion valve 65 is determined by changing the valve stroke to a predetermined value ST as shown in FIG.
When it exceeds 1, the increase rate of the refrigerant flow rate is set to increase rapidly. For example, a general electric expansion valve having a linear opening characteristic as shown in FIG. 10 and a solenoid valve are connected in parallel. A connection may be made to form a variable aperture. In this case, the solenoid valve may be opened when the throttle opening (valve stroke) of the electric expansion valve reaches a predetermined value.

In this embodiment, a fixed throttle (capillary 61) is provided in the refrigerant flow path between the outdoor heat exchanger 58 and the evaporator 31. However, as in the second embodiment of the present invention shown in FIG. The electronic expansion valve 6 for cooling is a variable throttle.
1 '(corresponding to the second throttle in the present invention), and the throttle opening of the expansion valve 61' is set to the electronic expansion valve 65 on the outlet side of the condenser 35 (hereinafter referred to as an electronic expansion valve for heating). May be controlled together with the throttle opening degree. The switching control of the electronic expansion valves 61 'and 65 and the four-way switching valve 57 at this time is performed as shown in Table 2 below according to the operation mode of the refrigeration cycle 55.

[0064]

[Table 2]

In this case, compared to the above embodiment, cooling,
Cycle matching in each defrosting mode can be more optimally performed, and temperature controllability in the dehumidifying mode can be further improved.

That is, in the dehumidification mode, the two electronic expansion valves 6
When the temperature of the outdoor exchanger 58 is raised or lowered with respect to the outside air temperature by arbitrarily controlling the combination of the opening degrees 1 'and 65, so that the outdoor exchanger 58 operates as an "outdoor condenser". To the case where it functions as an “outdoor evaporator” through the case where it operates as a “refrigerant passage”, the heat radiation ability of the condenser 35 and the heat absorption ability of the evaporator 31 can be adjusted according to the temperature and humidity conditions of the outdoor and the room. Can be adjusted in a wide range,
The temperature control range of the blown air in the dehumidification mode can be further expanded, and the temperature controllability can be further improved.

Hereinafter, a specific control example when the system configuration as shown in FIG. 11 is adopted will be described with reference to FIGS. FIG.
Indicates the control contents of the ECU 68. First,
This will be described. 12. However, since FIG. 12 includes the same parts as the control contents shown in FIG. 4, the same steps are denoted by the same step numbers and description thereof will be omitted, and only different parts will be described. In this embodiment, the cooling electronic expansion valve 61 'and the heating electronic expansion valve 65' are used.
Are set so as to be linear characteristics as shown in FIG.

If the branch destination in the step 200 is the cooling mode, after the execution of the step 211 for controlling the compressor rotational speed, the electronic expansion valve 6 for cooling is turned on.
Step 212 is executed to control the throttle opening of 1 'so as to be in an appropriate state according to the cooling load.

If the branch destination in step 200 is the dehumidification mode, after execution of step 232 for controlling the compressor speed, the cooling electronic expansion valve 6 is executed.
1 ', Steps 233 and 234 for controlling the throttle opening of the heating electronic expansion valve 65 are executed. Step 2 above
Details of the control contents at 33 and 234 are shown collectively in FIG. 13 and will be described below.

That is, in FIG. 13, it is determined whether or not the operation is the first operation after the dehumidification mode is selected (step 240). If it is the first operation, the valve is determined based on the inside air temperature Tr and the outside air temperature Tam at that time. Step 241 for determining an initial value of the opening (synonymous with the valve stroke, that is, the throttle opening) is executed.

Here, as shown in FIG. 16, the valve openings of the electronic expansion valves 61 'and 65 are, for example, four of A, B, C and D.
The electronic expansion valve 6 is controlled in stages.
As for the combinations of the valve opening degrees of 1 'and 65, five types of ranks 1 to 5 are set as shown in FIG. In step 241, the inside air temperature Tr and the outside air temperature Tam
And rank 1 based on the preset characteristics as shown in FIG.
5 is selected, whereby the initial value of the valve opening of each of the electronic expansion valves 61 'and 65 is determined. After the initial value of the valve opening is determined in this way, the process returns after executing step 246 for counting the elapsed time from the initial value.

After this, when step 240 is re-executed, "NO" is determined here, and in this case, step 242 for determining whether or not a predetermined time t has elapsed. Execute If the fixed time t has not elapsed, the process returns as it is. Therefore, the valve opening of each of the electronic expansion valves 61 'and 65 is maintained as it is until the fixed time t has elapsed. Will be.

When the predetermined time t has elapsed, in step 243, the difference temperature ΔT obtained by subtracting the actual condenser outlet temperature Tc from the target outlet temperature TAO is used as the identification value set in advance in consideration of the allowable range of the temperature control width. It is determined what relationship α has.

At this time, if there is a relationship of ΔT ≦ −α,
That is, when the actual outlet temperature from the air duct 21 indicated by the condenser outlet temperature Tc is higher than the target outlet temperature TAO, the step 244 of increasing the combination of valve opening degrees shown in FIG. 15 by one rank is executed. Step 2 to start counting the elapsed time later
It returns via 46. Therefore, for example, when the combination of the valve opening degrees is rank 3 (as can be understood from FIG. 15, the valve opening degree of the cooling electronic expansion valve 61 ′ is C, and the valve opening degree of the heating electronic expansion valve 65 is B. (If B <C))
The combination of those valve openings was changed to rank 4,
The valve opening of each of the electronic expansion valves 61 'and 65 is adjusted so that both of them become C. In addition, when the combination of the valve opening degrees is rank 5, the state is maintained.

When ΔT ≧ α, that is, when the actual outlet temperature is lower than the target outlet temperature TAO, the step 245 of reducing the combination of the valve opening degrees shown in FIG. After the execution, the process returns through step 246 to start counting the elapsed time. Therefore, for example, when the combination of the valve openings is in rank 3, the combination of those valve openings is rank 2 (the valve opening of the cooling electronic expansion valve 61 'is C, and the combination of the heating electronic expansion valve 65 is The valve opening is adjusted so as to be in the state (A). When the combination of the valve opening degrees is rank 1, the state is maintained.

Further, in the case of -α <ΔT <α, that is, when the difference between the actual blowing temperature and the target blowing temperature TAO is within an allowable range, the combination rank of the valve opening degree is maintained. The process returns through step 246 in the state.

As a result of the above-described control, when the defrosting mode is selected, the combination of the opening degrees of the cooling electronic expansion valve 61 'and the heating electronic expansion valve 65 changes for a predetermined time t. Each time the correction is made, it is corrected based on the amount of deviation between the actual outlet temperature and the target outlet temperature TAO. In this case, as shown in FIG. 17, each of the electronic expansion valves 61 ', 65
When the combination of the valve opening degrees changes between ranks 1 to 5, the condenser outlet temperature Tc and, consequently, the actual blowout temperature change. Therefore, when the above-described correction control is performed, Every time the predetermined time t elapses, the difference between the actual blow temperature and the target blow temperature TAO is reduced, and as a result, the control characteristic of the blow temperature can be greatly improved.

FIG. 18 shows the EC in the first embodiment.
A third embodiment of the present invention in which the control program of U68 is modified is shown, which will be described below. That is, in the third embodiment, steps 232 and 234 in the control program by the ECU 68 shown in FIG.
The feature is that the configuration is replaced with each step as shown in FIG. In FIG. 18, first, it is determined whether or not the operation is the first operation after the selection of the dehumidification mode (step 301). If it is the first operation, the evaporator intake air temperature T at that time is determined.
After returning to step 302, the initial value of the valve opening (synonymous with the throttle opening) of the electronic expansion valve 65 is determined based on the outside air temperature Tam. The initial value of the valve opening is, for example, the intake air temperature Tin and the outside air temperature T
It is determined based on a table showing the relationship between am and the preset multiple-stage valve opening.

After the execution of step 302 once, when step 301 is executed again, "NO" is determined here, and in this case, the evaporator outlet temperature Te (claim) Step 30 of adjusting the number of revolutions of the compressor 56 so that “evaporator temperature” in the invention of the fifth aspect becomes a set value.
3. Step 304 of adjusting the opening degree of the electronic expansion valve 65 so that the condenser outlet temperature Tc (that is, the blow-out temperature from the air duct 21) becomes the target blow-out temperature TAO which is a predetermined value.
And then returns.

According to the present embodiment having such a configuration,
The temperature of the condenser 35 can be maintained at an optimum state while the temperature of the evaporator 31 is kept stable by adjusting the rotation speed of the compressor 56. As a result, the temperature of the air blown out from the air duct 21 can be controlled. You can do it accurately.

FIG. 19 shows a fourth embodiment of the present invention in which the third embodiment is modified, and this will be described below. That is, the fourth embodiment is characterized in that the control program by the ECU 68 shown in FIG. 18 is replaced as shown in FIG. In FIG. 19, it is determined whether or not the operation is the first operation after the selection of the dehumidification mode (step 401). If it is the first operation, the electronic expansion is performed based on the evaporator intake air temperature Tin and the outside air temperature Tam at that time. After executing step 402 of determining the initial value of the valve opening of the valve 65 in the same manner as in the third embodiment, the process returns.

If "NO" is determined in step 401, the evaporator intake air temperature Tin (corresponding to "the air temperature upstream of the evaporator" in the invention of claim 6) and the evaporator outlet temperature Te (the invention of claim 6) Step 403 of adjusting the number of revolutions of the compressor 56 so that the temperature difference with the “air temperature after passing through the evaporator” becomes a set value, and the condenser outlet temperature Tc (that is, the temperature of air blown from the air duct 21) is adjusted. The target outlet temperature TAO which is a predetermined value
After the steps 404 for adjusting the opening of the electronic expansion valve 65 are sequentially executed such that

According to the present embodiment having such a configuration,
The heat exchange capacity of the evaporator 31 can be maintained at an optimum state while the heat exchange capacity of the evaporator 31 is stabilized by adjusting the rotation speed of the compressor 56. As a result, the temperature control of the air blown from the air duct 21 can be maintained. Can be performed accurately.

FIG. 20 shows a fifth embodiment of the present invention in which the third embodiment is modified, and this will be described below. That is, the fifth embodiment is characterized in that the control program by the ECU 68 shown in FIG. 18 is replaced as shown in FIG. In FIG. 20, it is determined whether or not the operation is the first operation after the dehumidification mode is selected (step 501). If it is the first operation, the electronic expansion is performed based on the evaporator intake air temperature Tin and the outside air temperature Tam at that time. After executing step 502 of determining the initial value of the valve opening of the valve 65 in the same manner as in the third embodiment, the process returns.

If "NO" is determined in step 501, the outside air temperature Tam (corresponding to the "outdoor temperature" in the seventh aspect of the invention) and the evaporator outlet temperature Te (the "evaporator passage in the seventh aspect of the invention"). Later air temperature)
Step 503 of adjusting the number of revolutions of the compressor 56 so that the temperature difference between the condenser 56 and the condenser 56 becomes the set value.
Step 504 of sequentially adjusting the opening degree of the electronic expansion valve 65 so that c (that is, the blowing temperature from the air duct 21) becomes the target blowing temperature TAO which is a predetermined value is sequentially performed, and the process returns.

According to the present embodiment having such a configuration,
Even when the outdoor air is blown into the room after heat exchange with the evaporator 31, the temperature of the condenser 35 can be maintained in an optimum state while keeping the heat exchange capability of the evaporator 31 stable, and as a result, It becomes possible to accurately control the temperature of the blown air from the blow duct 21.

FIG. 21 shows a sixth embodiment of the present invention in which the third embodiment is modified, and this will be described below. That is, the sixth embodiment is characterized in that the control program by the ECU 68 shown in FIG. 18 is replaced as shown in FIG. In FIG. 21, it is determined whether or not the operation is the first operation after the selection of the dehumidification mode (step 601). If it is the first operation, the electronic expansion is performed based on the evaporator intake air temperature Tin and the outside air temperature Tam at that time. After the step 602 of determining the initial value of the valve opening of the valve 65 in the same manner as in the third embodiment and the step 603 of counting the elapsed time from the initial value are sequentially executed, the routine returns.

If “NO” is determined in the step 601, a step 604 for determining whether or not a predetermined time t has elapsed is executed. If the fixed time t has not elapsed, the evaporator outlet temperature Te (corresponding to the "evaporator temperature" in the invention of claim 8) is adjusted to a set value to adjust the rotation speed of the compressor 56, step 605.
Steps 606 and 603 for sequentially adjusting the opening degree of the electronic expansion valve 65 so that the condenser outlet temperature Tc (the temperature of the air blown from the air duct 21) becomes the target blow-off temperature TAO, which is a predetermined value, are sequentially executed and the process returns.

When a predetermined time t has elapsed (step 60)
In the case of "YES" in step 4, the evaporator intake air temperature Tin ("the upstream air temperature of the evaporator" in the invention of claim 8)
) And the evaporator outlet temperature Te (corresponding to the “air temperature after passing through the evaporator” in the invention of claim 8) is adjusted to a set value, for example, 10 ° C., and the rotation speed of the compressor 56 is adjusted. Step 607, the step 608 of adjusting the opening of the electronic expansion valve 65 so that the condenser outlet temperature Tc becomes the target blowout temperature TAO, and the above-mentioned step 603 are sequentially executed and the routine returns.

According to the present embodiment having such a configuration,
At the beginning of the defrosting operation, the temperature of the condenser 35 can be maintained at an optimum state while the temperature of the evaporator 31 is kept stable by adjusting the rotation speed of the compressor 56. After elapse, the temperature of the condenser 35 can be maintained at an optimum state while keeping the heat exchange capacity of the evaporator 31 stable by adjusting the rotation speed of the compressor 56. As a result, the temperature of the blown air can be maintained. Control can be performed more accurately.

In the sixth embodiment, step 6
The control content at step 07 may be changed as shown in step 607 'as shown in FIG. That is, in this step 607 ', the compressor 56 is set so that the temperature difference between the outside air temperature Tam and the evaporator outlet temperature Te becomes the set value.
When such a change is made, even when the outdoor air is blown into the room after heat exchange with the evaporator 31, even if the air is blown into the room,
The temperature of the air blown from the air can be accurately controlled.

FIGS. 23 to 25 show a seventh embodiment of the present invention. Only the portions different from the first embodiment will be described below. That is, in the seventh embodiment, as shown in FIG.
Instead of the expansion valve 65 in the embodiment, a capillary 65 '(corresponding to a first throttle in the present invention) which is a fixed throttle is provided, and the capillary 65' and the outdoor heat exchanger 58 are provided.
Between the outdoor heat exchanger 58 and the capillary 6
It is characterized in that a check valve 93 for preventing the refrigerant from flowing into the 5 'side is provided.

In this case, in the dehumidification mode, the four-way switching valve 57 is switched to the position shown by the solid line (off position), and the solenoid valve 62 is turned off (the outdoor fan 89 is off). Therefore, the refrigerant discharged from the discharge port 56a of the compressor 56 flows through the condenser 35 → the capillary 65 ′ → the check valve 93 → the outdoor heat exchanger 58 → the capillary 61 → the evaporator 31 → the accumulator 90 → the suction port 56b of the compressor 56. Circulates in Thus, the air dehumidified and cooled by the evaporator 31 is blown into the room after being reheated to the target blowout temperature by the condenser 35.

The operation in the dehumidification mode will be described below with reference to specific numerical examples. That is, as schematically shown in FIG. 24A, the temperature of the indoor air that exchanges heat with the evaporator 31 is 25 ° C.
If the refrigerant evaporation temperature in the inside was 1 ° C., the air
After being dehumidified and cooled to, for example, 7 ° C. by heat exchange with the evaporator 31, it is reheated to about 41 ° C. by the condenser 35 and blown out into the room.

In this case, in the dehumidification mode, the capacitor 3
5 and the outdoor heat exchanger 58 function as a refrigerant condenser in a state of being connected in series, but actually, the capillary 6 is provided between the condenser 35 and the outdoor heat exchanger 58.
5 ′, most of the refrigerant (temperature is about 90 ° C.) discharged from the compressor 56
5, the condensation temperature in the condenser 35 is maintained at about 52 ° C., and the condenser 35 is re-heated by the heat of condensation as described above. The temperature of the refrigerant flowing out is reduced to about 18 ° C.

Accordingly, since a refrigerant having a relatively low temperature of about 18 ° C. flows into the outdoor heat exchanger 58, the difference between the refrigerant temperature and the outside air temperature is reduced. Here, as schematically shown in FIG.
° C, the temperature of the refrigerant flowing out of the outdoor heat exchanger 58 is reduced to about 17 ° C in accordance with the heat exchange between the outside air and the outdoor heat exchanger 58, and the outdoor heat exchanger 58 Is increased to about 16 ° C. That is, in a state where the difference between the temperature of the refrigerant flowing into the outdoor heat exchanger 58 and the outside air temperature is small, the amount of refrigerant condensed in the outdoor heat exchanger 58 is reduced. 58 can be regarded as a mere refrigerant passage pipe. FIG. 25 shows a Mollier chart of the refrigeration cycle in the dehumidification mode as described above for reference.

As a result, even when the outdoor heat exchanger 58 is arranged in a state where it receives the wind accompanying the running of the electric vehicle, the temperature of the condenser 35 in the dehumidifying mode hardly fluctuates according to the magnitude of the vehicle speed. The temperature of the wind after heat exchange with the condenser 35 becomes stable, and comfortable air conditioning can be expected.

Further, since only the capillaries 61 and 65 ', which are fixed throttles, need to be provided as the throttles provided in the refrigerant flow path, their structures can be simplified, which contributes to reduction of the manufacturing cost and the movable parts can be reduced. It is possible to reduce the number and improve the reliability with respect to the life.

In this embodiment, the outdoor heat exchanger 5
8 cannot perform the defrosting operation of supplying high-temperature gas refrigerant to remove frost on the outdoor heat exchanger 58,
Since the electric vehicle equipped with the air conditioner according to the present embodiment always has a standby time for charging, the outdoor heat exchanger 58 only needs to be defrosted during the standby time. Absent.

FIG. 26 shows an eighth embodiment of the present invention. Only the differences from the seventh embodiment will be described below. That is, FIG. 26 shows a schematic configuration of a main part of the air conditioner. In the ventilation duct 21 ′, the evaporator 31 is arranged on the upstream side, and the condenser 35 is arranged on the downstream side. In this case, the condenser 35 is
It is arranged with a predetermined bypass passage 94 between the side wall 1 'and the side wall 1'. The air damper 95 provided in the air duct 21 'is located at a position where the upstream side of the condenser 35 is closed (indicated by a two-dot chain line) during the cooling mode, and at a position where the bypass passage 94 is closed during the heating mode and the dehumidifying mode ( (Shown by a solid line).

The evaporator 31 and the condenser 35
The refrigerant circulation path of the refrigeration cycle 55 'including the discharge port 56a and the suction port 56b of the compressor 56
In between, the condenser 35, the capillary 65 ', the outdoor heat exchanger 58, the capillary 61, the evaporator 31, and the accumulator 90 are connected in this order, and the capillary 6 is connected.
5 ', a solenoid valve 65a is connected in parallel with the outdoor heat exchanger 58.
And an accumulator is connected to the solenoid valve 62.

The refrigeration cycle 55 'constructed as described above
In the operation state of the compressor 56, the refrigerant always flows through the condenser 35 in the operating state of the compressor 56. When the air heating by the condenser 35 is unnecessary as in the cooling mode, the air is damped by the air damper 95 on the upstream side of the condenser 35. To close. In the cooling mode, the solenoid valve 65a is turned on and the solenoid valve 62 is turned off. In the heating mode, the solenoid valve 65a is turned off and the solenoid valve 62 is turned on. 65
a and 62 are both switched off.

Therefore, particularly in the dehumidification mode, the refrigerant discharged from the compressor 56 is discharged from the condenser 35 → the capillary 65 ′ → the outdoor heat exchanger 58 → the capillary 61 → the evaporator 31 → the accumulator 90 → the compressor 5.
6, the same effects as in the seventh embodiment can be obtained.

FIG. 27 shows a ninth embodiment of the present invention. Only the portions different from the eighth embodiment will be described below. That is, this embodiment is based on the premise that the wind passing through the evaporator 31 is heated using the combustion type heating unit 96. Specifically, as shown in FIG. 27, a hot water heater 96a of the combustion type heating unit 96 is provided as a heat source in place of the condenser 35 in the eighth embodiment in a ventilation duct 21 'provided with an evaporator 31 and an air damper 95. Has been arranged.

In addition to the hot water heater 96a, the combustion type heating unit 96 includes a combustion type heater 96b to form a closed loop through which water flows together with the hot water heater 96a.
Heat exchanger 96c, pump 96d, solenoid valves 96e and 96
By switching the operating state of the pump 96d and the open / close state of the solenoid valves 96e and 96f, hot water heated by the combustion heater 96b or hot water heated by the heat exchanger 96c is selected as the hot water heater 96a. It is configured to be circulated periodically.

The evaporator 31 and the heat exchanger 9
The refrigerant circulation path of the refrigeration cycle 98 including the condenser 97 functioning as the heat source of the condenser 6c includes a condenser 97, a capillary 65 ', an outdoor heat exchanger 58, and a capillary between the outlet 56a and the inlet 56b of the compressor 56. 61, the evaporator 31, and the accumulator 90 are connected in this order, the solenoid valve 65a is connected in parallel with the capillary 65 ', and the solenoid valve 62 is connected between the outdoor heat exchanger 58 and the accumulator. .

In the above configuration, in the cooling mode,
The compressor 56 is operated on the refrigeration cycle 98 side, and the solenoid valve 65a is switched on and the solenoid valve 62 is switched off. On the combustion type heating unit 96 side, the combustion type heater 96b and the pump 96d are stopped. By turning off both the solenoid valves 96e and 96f, the supply of the hot water to the hot water heater 96a is stopped.

Further, in the heating mode using the combustion type heater 96b, the compressor 56
Is maintained in an operation stop state (the solenoid valves 65a and 62
Is off), on the combustion type heating unit 96 side, the combustion type heater 96b and the pump 96d are operated, and the solenoid valve 9 is operated.
6e is turned on and the solenoid valve 96f is switched off, so that the hot water heated by the combustion heater 96b is heated by the hot water heater 96a → the pump 96d → the solenoid valve 96e.
→ Circulate in the order of the combustion type heater 96b.

Further, in the heating mode using the heat pump function of the refrigeration cycle 98, the compressor 56 is operated on the refrigeration cycle 98 side and the solenoid valve 65a is operated.
Is turned off, and the solenoid valve 62 is turned on, so that the condenser 97 functions as a heat source of the heat pump cycle, and the outdoor heat exchanger 58 is maintained as a function of “evaporator”, while the combustion type heating is performed. On the unit 96 side, the pump 96d is operated while the operation of the combustion heater 96b is stopped, and the solenoid valve 96 is operated.
e in the off state and the solenoid valve 96f in the on state, the condenser 97
The hot water heated by the heater is supplied to a hot water heater 96a → pump 9
The circulation is performed in the order of 6d → the solenoid valve 96f → the heat exchanger 96c.

In the dehumidification mode, the compressor 56 is operated on the refrigerating cycle 98 side, and the solenoid valves 65a and 62 are both turned off, so that the condenser 97 functions as a heat source of the heat pump cycle and the evaporator is operated. On the combustion heating unit 96 side, the pump 96d is operated while the combustion heater 96b is stopped, and the solenoid valve 96e is turned off and the solenoid valve 96f is turned on on the combustion heating unit 96 side. Thus, the hot water heated by the condenser 97 in the heat exchanger 96c is circulated in the order of the hot water heater 96a → the pump 96d → the solenoid valve 96f → the heat exchanger 96c.

Therefore, in the dehumidification mode, the air dehumidified and cooled by the evaporator 31 is reheated by the hot water heater 96a and blown out into the room. In this case, however, the heating source of the hot water heater 96a is also used. The capillary 6 is provided between a certain condenser 97 and the outdoor heat exchanger 58.
Since 5 'is provided, similar to the seventh embodiment,
The outdoor heat exchanger 58 can be regarded as a mere refrigerant passage pipe. Therefore, even when the outdoor heat exchanger 58 is arranged in a state of receiving the wind accompanying the traveling of the automobile, the temperature of the condenser 97 in the dehumidifying mode is less likely to fluctuate according to the magnitude of the vehicle speed, and is heated by the condenser 35. Since the temperature of the blown air after heat exchange with the hot water heater 96a becomes stable, comfortable air conditioning can be expected.

The present invention is not limited to the above embodiments, but can be modified or expanded as follows. The evaporator target outlet temperature Teo in the dehumidifying mode was calculated so as to satisfy the intake air temperature Tin-15 ° C. and 3 ° C. or more.
eo may be changed according to the outside air temperature or the indoor humidity.

The automatic switching of the operation mode when the DEF input is present has been described.
For example, when the dehumidification switch or the auto air conditioner switch is turned on, the operation mode may be automatically switched as in the above embodiment.

In step 155, the blowing air amount VAO at the time of DEF is set to a constant value (for example, 300 m ³ / h). However, the blowing air amount VAO may be changed according to the required heat amount QAO. Similarly, the opening degree of the inside / outside air damper 25 determined in step 165 may be changed without being fixed to the outside air mode.

In each of the above-described embodiments, the combination of the valve opening degrees of the electronic expansion valve is corrected based on the condenser outlet temperature Tc, which is information indicating the temperature of air blown out from the air duct 21. The correction may be made based on other information having a phase relationship with the temperature (for example, a high pressure such as a compressor discharge pressure). The combustion type heating unit 96 adopted in the ninth embodiment may be used as a heating source in the first and second embodiments.

Further, FIG. 4, FIG. 12, FIG. 13 and FIG.
22 to 22 may be realized by independent circuit means. In addition, the application target is not limited to the air conditioner of the electric vehicle, and may be applied to various types of air conditioners such as an air conditioner of an engine driven vehicle and an air conditioner of a house.

[0117]

As is apparent from the above description, according to the present invention, the first throttle is provided in the refrigerant flow path between the condenser and the outdoor heat exchanger, and the first throttle is provided between the outdoor heat exchanger and the evaporator. An air conditioner in which an operation mode is switched to one of cooling, heating, and dehumidification by providing a second throttle in a refrigerant flow path therebetween and switching a valve provided in a refrigerant circulation circuit to switch a refrigerant circulation path. In the device, in the dehumidification mode, the refrigerant flows from the condenser to the evaporator via the first throttle, the outdoor heat exchanger, and the second throttle in this order. Even when the air conditioner is installed in a state in which the wind accompanying the heat affects the heat radiation system of the refrigerant circuit, it is possible to effectively prevent a situation in which the blowout temperature in the dehumidification mode fluctuates depending on the magnitude of the vehicle speed. As to become capable of performing such air conditioning operation.

When both the first and second diaphragms are constituted by fixed diaphragms, the structure of those diaphragms can be simplified, which contributes to a reduction in manufacturing cost and reduces the number of movable parts. As a result, the reliability of the life can be improved.

Further, the temperature of the blown air in the dehumidification mode is controlled by a first air conditioner provided between the condenser and the outdoor heat exchanger.
By adjusting the throttle opening of the throttle, the heat dissipation capacity of the condenser and the heat absorption capacity of the evaporator can be adjusted in a relatively wide range, so that the temperature of the blown air in the dehumidification mode can be adjusted. The width can be increased, and the temperature controllability in the dehumidification mode can be improved.

In this case, at least the first
By controlling the throttle opening of the throttle and controlling the number of revolutions of the compressor, the refrigerant discharge pressure of the compressor can be adjusted, and the evaporator temperature can be sufficiently dehumidified within a range that is not excessively cooled. The temperature of the condenser can be controlled to an appropriate temperature while controlling the temperature of the condenser so as to be equal to the target temperature, and the comfort in the dehumidification mode can be further improved. .

In particular, in the dehumidification mode, in adjusting the compressor speed as described above, the compressor speed is controlled so that the evaporator temperature becomes the set value, the upstream air temperature of the evaporator and the passage through the evaporator. A configuration in which the number of rotations of the compressor is controlled so that the temperature difference from the air temperature afterwards becomes a predetermined value, and the number of rotations of the compressor is controlled so that the temperature difference between the outdoor temperature and the air temperature after passing through the evaporator becomes a predetermined value. In addition to adopting any one of the configurations for controlling the opening of the first throttle, at least in adjusting the opening of the first throttle as described above, the opening of the first throttle is controlled so that the temperature of air blown from the air duct becomes a predetermined value. If the configuration is such that the degree is adjusted, the temperature of the blown air can be accurately controlled.

Further, in the dehumidification mode, when adjusting the compressor speed and the opening degree of the first throttle as described above, the period from the start of the dehumidification operation to the elapse of a predetermined time is determined by the evaporator operation. The number of rotations of the compressor is controlled so that the temperature becomes a set value, the opening degree of the first throttle is adjusted so that the temperature of air blown from the air duct becomes a predetermined value, and the predetermined time has elapsed. Later, while controlling the rotation speed of the compressor so that the temperature difference between the upstream air temperature of the evaporator and the air temperature after passing through the evaporator becomes a predetermined value, the blowout temperature from the air duct becomes the predetermined value. If the opening degree of the first throttle is adjusted, the temperature of the blown air can be controlled more accurately.

The first throttle and the second throttle provided in each refrigerant flow path between the condenser and the outdoor heat exchanger and between the outdoor heat exchanger and the evaporator are both constituted by variable throttles. In the dehumidification mode, the temperature of the evaporator and the temperature of the condenser are adjusted by correcting the combination of the throttle openings of the respective throttles based on information indicating the temperature of the air blown out of the air duct every predetermined time. With this configuration, the actual blowout temperature can be brought closer to the target blowout temperature every time a predetermined time elapses, and the control characteristics of the blowout temperature can be greatly improved.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of an entire air conditioner showing a first embodiment of the present invention.

FIG. 2 is a front view of an air conditioner control panel.

FIG. 3 is a diagram illustrating a relationship between an operation mode of a refrigeration cycle and an operation mode of an outdoor fan.

FIG. 4 is a flowchart of a control program.

5A is a diagram showing a relationship between a set thermal sensation Sset and Tset ′, FIG. 5B is a diagram showing a relationship between an outside air temperature Tam and ΔTam, and FIG. 5C is a diagram showing a relationship between the solar radiation Ts and ΔTs. Figure showing

FIG. 6 is a diagram showing a relationship between a required heat quantity QAO and an air volume VB.

FIG. 7 is a diagram showing a relationship between a blown air amount VAO and a blower voltage;

FIG. 8 is a diagram showing the relationship between the compressor rotation speed, the evaporator outlet temperature, and the condenser outlet temperature using the throttle opening of the electronic expansion valve as a parameter.

FIG. 9 is a diagram showing a relationship between a valve stroke (throttle opening) of an electronic expansion valve and a refrigerant flow rate.

FIG. 10 is a diagram showing a relationship between a valve stroke (throttle opening) of an electric expansion valve used in an example in which the first embodiment is partially modified and a refrigerant flow rate.

FIG. 11 is a schematic configuration diagram of an entire air conditioner showing a second embodiment of the present invention.

FIG. 12 is a flowchart of a control program.

FIG. 13 is a flowchart of a main part of the control program.

FIG. 14 is a diagram showing a relationship between an inside air temperature Tr and an outside air temperature Tam and a combination rank of valve opening degrees of two electronic expansion valves.

FIG. 15 is a diagram showing contents of a combination rank of valve opening degrees of two electronic expansion valves.

FIG. 16 is a diagram showing a relationship between a valve opening degree of an electronic expansion valve and a refrigerant flow rate.

FIG. 17 shows the relationship between the compressor rotation speed and the evaporator outlet temperature, and shows the relationship between the compressor rotation speed and the actual blowing temperature from the air duct using the combination rank of the valve opening degrees of the two electronic expansion valves as a parameter. Illustration

FIG. 18 is a flowchart of a main part of a control program showing a third embodiment of the present invention.

FIG. 19 is a flowchart of a main part of a control program showing a fourth embodiment of the present invention.

FIG. 20 is a flowchart of a main part of a control program showing a fifth embodiment of the present invention.

FIG. 21 is a flowchart of a main part of a control program showing a sixth embodiment of the present invention.

FIG. 22 is a view corresponding to FIG. 21 showing a modification of the sixth embodiment.

FIG. 23 is a schematic configuration diagram of a main part of an air conditioner according to a seventh embodiment of the present invention.

FIG. 24 is a schematic diagram for explaining the operation.

FIG. 25 is a Mollier chart in a dehumidification mode.

FIG. 26 is a schematic configuration diagram of a main part of an air conditioner according to an eighth embodiment of the present invention.

FIG. 27 is a schematic configuration diagram of a main part of an air conditioner according to a ninth embodiment of the present invention.

[Explanation of symbols]

22: outside air suction port, 23, 24 ... inside air suction port, 25 ... inside / outside air damper, 31 ... evaporator, 35, 97 ... condenser, 40 ... DEF outlet, 41 ... FACE outlet, 4
6: intake air temperature sensor, 52: FOOT outlet, 55, 5
5 ', 98: refrigeration cycle, 56: compressor, 57
... four-way switching valve, 58 ... outdoor heat exchanger, 61 ... capillary (second throttle), 61 '... cooling electronic expansion valve (second throttle), 65 ... electronic expansion valve (first throttle), 65 '... Capillary (first aperture), 67 ... Inverter, 68 ... EC
U (control means), 77 ... inside air temperature sensor, 78 ... outside air temperature sensor, 79 ... solar radiation sensor, 80 ... evaporator outlet temperature sensor, 81 ... condenser outlet temperature sensor, 82 ...
82a: Cooling key, 82b: Warm key, 84: Hot feeling display unit, 88: Refrigerant pressure sensor, 89 ...
Outdoor fan, 96 ... combustion heating unit.

Continuation of front page (56) References JP-A-5-178069 (JP, A) JP-A-5-178078 (JP, A) JP-A-5-319077 (JP, A) JP-A-4-151324 (JP, A) JP-A-5-229333 (JP, A) JP-A-5-96940 (JP, A) JP-A-5-141788 (JP, A) JP-A-62-252344 (JP, A) 3-67964 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) B60H 1/32 624

Claims (9)

(57) [Claims] An evaporator disposed in a blower duct, a condenser functioning as a heating source for wind passing through the evaporator, and an outdoor heat exchanger disposed outside the blower duct. And a first throttle is provided in a refrigerant flow path between the condenser and the outdoor heat exchanger, and a second throttle is provided in a refrigerant flow path between the outdoor heat exchanger and the evaporator, In an air conditioner that switches an operation mode to one of cooling, heating, and dehumidification by switching a refrigerant circulation path by switching a valve provided in the refrigerant circulation circuit, in the dehumidification mode, refrigerant is supplied from the condenser. The first
The air conditioner is configured to flow through the throttle, the outdoor heat exchanger, and the second throttle to the evaporator in this order. 2. The air conditioner according to claim 1, wherein the first throttle and the second throttle are both constituted by fixed throttles. 3. The first stop and the second stop,
At least the first throttle is configured as a variable throttle, and the temperature of the evaporator and the temperature of the condenser can be adjusted by adjusting the aperture of the first throttle in the dehumidification mode. The air conditioner according to claim 1. 4. A configuration in which the number of revolutions of a compressor provided in the refrigerant circuit is adjustable, and at least the aperture of the first aperture is controlled in a dehumidifying mode, and the number of revolutions of the compressor is also reduced. The air conditioner according to claim 3, further comprising control means for controlling. 5. In the dehumidification mode, the control means controls at least the number of revolutions of the compressor so that the temperature of the evaporator becomes a set value, and controls the temperature of air blown from the air duct to a predetermined value. The air conditioner according to claim 4, wherein the air conditioner is configured to adjust at least the aperture of the first aperture. 6. The control means controls at least the rotation speed of the compressor so that a temperature difference between an air temperature upstream of the evaporator and an air temperature after passing through the evaporator becomes a predetermined value in a dehumidification mode. 5. The air conditioner according to claim 4, wherein at least an opening degree of the first throttle is adjusted so that a temperature of air blown from the air duct becomes a predetermined value. 7. The control means controls at least the number of revolutions of the compressor so that a temperature difference between an outdoor temperature and an air temperature after passing through the evaporator becomes a predetermined value in the dehumidification mode, and controls the air duct. The air conditioner according to claim 4, wherein at least the degree of opening of the first throttle is adjusted so that the temperature of the air blown from the first throttle reaches a predetermined value. 8. In the dehumidification mode, the control means controls at least the number of revolutions of the compressor so that the temperature of the evaporator becomes a set value during a period from the start of the dehumidification operation to the elapse of a predetermined time. The throttle opening of the first throttle is adjusted at least so that the temperature of air blown from the air duct becomes a predetermined value, and after the predetermined time has elapsed, the air temperature on the upstream side of the evaporator and the air temperature after passing through the evaporator are reduced. At least the rotation speed of the compressor is controlled so that the temperature difference with the air temperature becomes a predetermined value, and at least the opening degree of the first throttle is reduced so that the temperature of air blown from the air duct becomes a predetermined value. 5. The method according to claim 4, wherein the adjusting is performed.
An air conditioner as described. 9. A method according to claim 1, wherein said first diaphragm and said second diaphragm are both constituted by variable diaphragms, and a combination of diaphragm openings of said respective diaphragms is set in a plurality of stages. In the method, the temperature of the evaporator and the temperature of the condenser are corrected by correcting the combination of the opening degrees of the first throttle and the second throttle based on the information indicating the temperature of the air blown out from the air duct every predetermined time. 2. The apparatus according to claim 1, wherein the apparatus is configured to be able to adjust the distance.
An air conditioner as described.